Grinding machine



Nov. 21, y1933. H,l R; .SLER 1,935,633

@BINDING rukcnnus Filed Dec. 31, 1931 6 sheets-sheet 1 lnvenitor lGtforn'eg No'v. 21, 1933. H. R. lsLER GRINDING mamma Filed Dec. 51, 19316 Sheets-Sheet 2 3 nveutor HEP/MM ,Q ffm@ Gttomeg H. R. lsLER 1,935,633

4 I GRINDING IACHINE Filed Dec. 31, 1931 6 Sheets-Sheet 3 //ll//ll//llll Nav. 21, 1933.

nventor #fem/v 2 [51,52

Gttorneg Npv. 21, 1933.

H. R. ISLER GRINDING nenni:

Filed Dec.

31, 1931 6' Sheets-Sheet 5 z: H3 a 1,12

nvmtor HEP/MN ,e 131,519' -mvkmttorm Nov. ,21, 1933.` t im. .su-:R1,935,633-

.GRINDING IACHINE :inventor Hmm/v 2. [fue a,-v v

attorney Patented Nov. 21, 1933 UNITED STATES GRINDING MACHINE Herman R.Isler, Norwood, Ohio, assignor to The Cincinnati Milling MachineCompany, Cincinnati, Ohio, a corporation of Ohio Application December31, 1931 Serial No. 584,189

21 Claims.

This invention relates to grinding machines and more particularly to animproved cutter grinder that may be utilized not only for sharpeningcutters but for general purposes such as cylindrical and plane surfacegrinding operations.

An object of this invention is to provide a grinder for the purposesstated, having a simple and compact transmission for effecting powermcvement of the table in a plurality of selective automatic cycles.

Another object of this invention is to provide an improved mechanism foreffecting relatively large increments of feed with respect to a surfacegrinding wheel without increasing the length of the normal or necessarygrinding strok'. of the work.

A further object of this invention is to provide an improvedhydraulically actuated cross feed mechanism for a surface grindingmachine.

An additional object of this invention is to provide a simplified andimproved hydraulic variable feed transmission for a reciprocatinggrinding machine table having a cycle selector whereby the table may beautomatically reversed at each end of its stroke; or at either end witha subsequent stop at the end of the succeeding stroke; or an automaticstop at the end of each stroke.

Other objects and advantages of the present 30 invention should bereadily apparent by reference to the following specification consideredin conjunction with the accompanying drawings illustrative of oneembodiment thereof, but it will be understood that any modifications maybe made in the specific structural details within the scope of theappended claims without departing from or exceeding the spirit of theinvention.

Referring to the drawings in which like reference numerals indicate likeor similar parts:

Figure 1 is an elevation of a grinding machine embodying the principlesof this invention.

Figure 2 is a plan View of the machine shown in Figure 1.

Figure 3 is a section through the feed transmission box as viewed on theline 3 3 of Figure 2.

Figure 4 is a detail sectional view through the reverser valve shown inFigure 3.

Figure 5 is an expanded view of the cycle selector drum.

Figure 6 is an expanded View of the feed transmission for the table.

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Figure 7 is a detail view of the detent mechal nism for the reversinglever.

Figure 8 is a sectional view on the line 8-8 of Figure 3.

Figure 9 is a sectional view through the feed box showing the relief andthrottle valves partly in section as viewedv on the line 9-9 of Figure8. 60

Figure 10 is a plan View partly in section showing the cross feedmechanism.

Figure 11 is a section on the line 11-11 of Figure 10. Y

Figure 12 is a section on the line 12-12 of 65 Figure 11.

Figure 13 is a section on the line 13-13 of Figure 11.

Figure 14 is a detail section on the line 14--14 of Figurel 13.

Figure l5 is a detail section on the line 15-15 of Figure 3.

Figure 16 is a detail View showing the indicia on the throttle valveindicator dial.

Referring to Figure 1 of the drawings, the reference numeral 10indicates the base of the v machine having guideways .1.1 formed uponthe -top thereof for receiving a reciprocating saddle 12. A Wheel head13 is adjustably mounted on the bed of the machine for verticaladjustment or rotatable adjustment relative to the saddle but themechanisms for effecting these adjustments are not shown as they do notconstitute any part of this invention. A prime mover, not shown, ismounted in the bed for effecting rotation of the grinding wheel.

A Work table 14 is reciprocably mounted on the saddle for transversemovement relative to the grinding wheel 15 journaled in the head 13.

'A self-contained hydraulic transmission is mounted in a. transmissionhousing or casing 16 depending from the under side of the saddle, asmore particularly shown in Figure 3, for effecting reciprocation of -thework table. Fluid pressure is generated by an hydraulic pump 1'7 whichis driven from a prime mover, such as an electric motor 18, mounted'inan exterior pocket 19 formed in the wall of the transmission casing. Thearmature shaft 20 of this motor projects into the housing Where it isprovided with a spiralA gear 21 meshingwith the spiral gear 22 securedto the end of the pump drive shaft 23. Actuation of the electric motorwill theref ore effect continuous rotation of the pump. This pump may beof any suit-able construction, the one illustrated being a constantdelivery gear type pump. The lower part of the transmission casingconstitutesv a uid reservoir 134 from which oil is drawn through thepump intake 24 and forced under pressure through the conduit 24 to arelief valve 25 shown more particularly in Figure 9. The reservoir isfilled by removing plug 135, and a gauge glass 136 serves to indicatethe oil level, a drain plug 137 is provided in the bottom of thereservoir.

The relief valve is provided with a. reciprocation plunger 26 which isnormally held in position by means of spring 28 to close overflow outlet27. 'I'his valve permits escape of fiuid from the system when thepressure therein has reached a predetermined maximum as determined bythe setting of the spring 28. This setting may be varied by theadjusting screw 28'. A port 29 formed in the side of the valvecommunicates with a throttle valve 30 in which is reciprocably mounted atapered valve plunger 31. This plunger is provided with a taperedportion 32 which determines the amount of ow throughthe port and therebythe rate of movement of the table, and a reduced annular portion 32'around which the fluid pressure will flow when the valve is in an openposition as shown in Figure 9 thereby conducting the fluid to 'channel33. The valve plunger 31 is formed on one end with a plurality of rackteeth 34 engageable by rack pinion 35 formed on the end of a rotatableshaft 36. This shaft projects through a bushing 36 in the forward wallof the casing and has keyed thereto a knurled ad justing knob 37 and hasthreaded on the end thereof a locking nut 37. As shown in Figure 16, theprojecting end of the bushing has a reference mark scribed thereon whilethe knob 37 is provided with lindiciaI marks cooperating with thereference mark to show the rate at which the table will move for eachsetting. It

is apparent that rotation of the knob will ef-A fect longitudinalmovement of the valve and thus vary lthe opening of port 29 and the fiowof fluid to the motor; Tightening of the locking nut 37' serves to holdthe valve in its adjusted position.

The channel 33 conducts the fluid to a reversing valve 38 as shown inFigure 8 which demotor 39. As shown in Figure 4, a valve piston 40 isreciprocably mounted in the reversing valve housing and isiprovided withan annular groove 41 whereby upon movement of the valve to the right asviewed in this figure, the uid will be conducted to channel 42 leadingto one to the left, the fluid in channel 42 will escape to the exhaustport 47. Thus shifting of the valve from one extreme position to theother will change the direction of motor rotation, while movement to acentral or neutral position will cut off all flow to the motor and thetable will stop.

The motor 39 may be of any suitable construction in which aconstantiflow of fluid pressure therethrough will effect rotation of themo. tor shaft. In the present instance this motor is of the gear typeand the method of operation is that the uid pressure from channel 33will flow through the reversing valve in channel 75 43 to effectrotation of the motor shaft in one termines its direction of flow to thehydraulic exhaust port 46 and similarly, upon movement direction, theexhaust fluid returning through channel 42 and port 47 to the reservoir.Shift'- ing of the reversing valve will cause a reverse direction of owthrough the motor rotating the motor shaft in the opposite direction,the exhaust uid returning through channel 43 to reservoir. The speed ofrotation of the motor may be varied by adjusting the throttle valve 31by means of the control knob-37 located on the front of the machine.

The motor shaft 48 as shown in Figure 3 is provided with a spiral gear49 which meshes with a spiral gear 50 mounted for free rotation on thehorizontal shaft 5l upon assembly of detachable housing 16 with thesaddle. The gear 50 is fixed to the sleeve 52 which has clutch teeth 53formed on the end face thereof. Fixed to the shaft 51 is a selectorclutch member 54 having clutch teeth 55 formed on the end thereof forengaging the clutch teeth 53 and thereby coupling the gear 50 to theshaft 51. This coupling is effected by longitudinally sliding the shaft51 by means of the control knob 56. Keyed to the end of the shaft 51 isa pinion 57 which meshes with a rack 58 xed to the under side of thetable 14. From the foregoing it will be seen that a variable speedhydraulic transmission has been provided for the table, ,comprising apump and a motor, and means to vary the fiow of the pump fluid to themotor together with a relief valve permitting the discharge to reservoirof excess fluid and a selector clutch by which the motor may beselectively coupled to the table for actuation thereby.

The shiftable clutch member 54 has integrally 110 formed therewith agear 59 which meshes with a pinion 60 forming part of a gear couplet,the other member 61 of which meshes with a gear 62 fixed to the end of ashaft 63. This shaft extends through the front wall of the housing andhas 115 xed to its cuter end the hand wheel 64. Upon movement of theclutch to the position shown in Figure 6, it will be seen that the gear59 is in mesh with the gear 60 whereby rotation of the hand wheel 64will effect longitudinal movement of the 120 table through the geartrain just described. The member 54 may also be' moved to a neutralposition in which the gear 59 will be out of mesh with the gear 60 andthe clutch teeth 55 out of mesh with the clutch teeth53. In thisposition of the clutch, the table 14 may be manually pushed or pulledback and forth as when the machine is utilized for cutter grindingpurposes. In order to maintain the shaft 51 in any one of its threepositions, three annular grooves 65 are formed on the shaft and a springpressed pawl or detent 66 is mounted in the shaft bushing for engagingany one of these groovesto thereby maintain the shaft in any one of itsshifted positions.

The reverse valve plunger is shifted back and 135 forth by means of thefollowing mechanism. A' shifter rod 67 is rotatably and reciprocablymounted in the upper part of the saddle and provided with a cycleselector drum 68 which is pinned to the shaft for axial and rotativemovement therewith.V As shown in the expanded view in Figure 5 theselector drum is provided with a peripheral groove 69 for receiving theshifter pin 70 secured to the end of the valve plunger 40. A secondannular groove 71 is formed in the periphery of .the selector drum forreceiving the depending pin 72 of the reversing lever 73. As shown inthe development of the drum in Figure 5, the circumference thereof isdivided into four equal sectors by longitudinal or detent grooves '14,'15, 'is and '17. 150

Each of these grooves are 90 apart which makes it possible to rotate theshifter rod 6'1 to any one of four different positions, and a springpressed detent 78 as shown in Figure 15 will maintain the rod in thatposition. 'If 4the shifter rod 67 is rotated to such a position that thegroove is coplanar with the pin '70, extending into the groove 69, itwill be apparent that oscillation of the control lever 73 willimmediately effect lateral movement of the pin '72 and longitudinalshifting of the reversing valve. If the shifter rod 67 is now rotatedthrough a 90 arc in either a clockwise or a counter-clockwise direction,either the groove 76 or the groove 74 will then be coplanar with the pin'70. In either one of these positions, it will be seen that a recesssuch as 79 or 79' formed in the sides of the groove will be opposite tothe pin. These recesses permit a certain amount of lost motion betweenthe pin 70 and the side of the slot, which must be taken up beforemovement of the valve begins. This permits shifting by the usual loadand fire mechanism shown in Figure '1. Movement of the pin '72*away fromgroove '79 or 79' will cause its engagement with the straight wall ofthe slot, as in the rst instance, which will thereby move the valve to aneutral position.

A further rotation of the rod 67 through an angle of 90 in the samedirection as the first movement will bring the pin 70 coplanar with thegroove '77 and in that position it will be noted that there is a recessformed in the groove 69 on each side of the pin 70. This permits lostmotion on each side of the pin 70 whereby the valve may be shifted byload and fire mechanism in either direction thereby making it possibleto effect a reciprocating cycle. The reversing control lever '73 ispivotally mounted in the upper wall of the housing on one end of a pin80 which has fastened to the lower end, by means of a tapered pin 81, adetent member 82. A spring pressed detent 83 is mounted in cooperativeengagement with the detent for maintaining the same in either one of twopositions and by means of its cam shaped end will serve to re the leverfrom one position to the other upon an angular movement suicient to movethe pointed end of the detent 83 past the peak 84 formed on the detent.

A reciprocable member 85 is mounted in the hollow of the reversing lever73 and is maintained in a projecting position beyond the end thereof bya spring 86 interposed between a shoulder 87 formed on the member and aplug 88 xed in the end of the lever 73. This projecting end 89 isadapted to be engaged by suitably positioned dogs 90 mounted in T slots91 formed in the front side of the table. By means of this mechanism thereversing valve may be manually or automatically controlled; and, bysuitably positioning the cycle selector drum, any one of four cycles ofmovement may be obtained. These -cycles comprise a constantlyreciprocatingcycle corresponding to detent '77 in which the table isautomatically reversed at the end of each stroke; a one-way cycle inwhich the table is reversed at the end of one stroke and stopped at theend of the succeeding stroke. This one-way cycle may be effected so thatthe automatic reverse will take place at either the right hand end ofthe table corresponding to detent '76 or at the left hand end of thetable corresponding to detent '14. The selector drum may also be set tostop the table at the end of each stroke, corresponding to detent 75, inwhich case no automatic reverse will take place; but it will benecessary for the operator to longitudinally shift the rod 67 in thedirection in which he desires the table to move.

As shown in Figure 2 the shifter rod 67 extends to opposite ends, of thetable whereby the operator, if standing at either end of the table orupon either side thereof, may reach the control knobs 92 secured toopposite ends of the rod 67 and longitudinally shift the reversing valveto start the table or change its direction of movement. When the machineis utilized for cutter grinding purposes the operator usually stands atthe rear of the table and holds the work with his right hand in whichcase he may not be able to reach the control knob 92. For this reason ashaft 93 is rotatably mounted upon the side of the machine and providedon one end with a bifurcated lever 94 engaging the end of the shifterrod 67 and on the other end with a control lever 95. By this means theoperator may move the shifter rod 67 with his left hand while holdingthe Work with his right hand.

The saddle 12 is reciprocably mounted upon the bed 10 as previouslyexplained and this movement may be effected by means of a feed screw 96journaled at opposite ends in the saddle and engaging a nut 97 fixed inthe bed. Hand wheels 98 are keyed to opposite ends of the feed screw foreffecting rotation of the screw and thereby movement of the saddle froman operating position at either the front or rear of the machine. A sshown in Figure 10 the shaft 96 is also provided with a dial 99 forindicating the amount of movement effected in the saddle.

For imparting increments of feed to the saddle to effect transverseadjustment of the table, the shaft 96 has k'eyed thereto a spur gear 100which meshes with a gear 101 secured to the stub shaft 102 as shown inFigure 13. As shown in this figure the gear 101 is provided with anelongated hub 103 in which is formed a pair of segmentalgrooves 104 and105. These grooves arev axially spaced and are formed on diametricallyopposite sides of the hub. In each groove a latch dog or double pawl 106is pinned to a shaft 107 vfor pivotal movement, the shaft having apinion gear 108 secured to the end thereof. 'I'he pinion gears 108 and108' mesh with gear teeth 109 formed on the end of the member 110 whichis mounted for free rotation on the shaft 102. A control knob 111 issecured to the periphery of the member 110 and has a ange 112surrounding the pinion gears 108 and 108. Each latch dog 106 is providedwith a pair of flat angular surfaces 113 alternately engageable by aspring pressed strip 114. This strip is engaged at opposite ends -bysprings 115 which are positioned beyond the latch dog so that as the dogis turned from one position to the other the pressure will be brought tobear near the center of the strip. Each of these at surfaces 113terminates in a pawl 116 which is engageable in notches 117 formedinteriorly of the trigger gears 118 and I118. Upon rotation of the gear118 in a counter-clockwise direction as` viewed in Figure 14,

it will be seen that the dog 106 Will be slightly rotated in acounter-clockwise direction against the pressure of the springs 115 andthe pawl will ratchet by the notches; while upon rotation of the gear ina clockwise direction the dog 106 L would tend to be rotated in aclockwise `direction but since the fiat surface 113 bearing againststrip 114 will prevent this movement, the gear 101 will be rotated withthe gear 118.

The gear 118 meshes directly with a rack bar 119 while the gear 118 isoperatively connected to the rack bar 120 thru an intermediate pinion121 shown in Figure 12. Each of these rack bars are reciprocably mountedin separate cylinders 122 and 123 formed in the casting 124 attached tothe saddle. The rack bars are in the form of pistons and admission ofpressure to one end of the cylinders will effect simultaneousreciprocation of the rack bars in the same direction and rotation of themechanism coupled therewith. In order to limit the longitudinal movementof the rack bars and thereby predetermine the amount of rotation to beimparted to the trigger gears, adjustable stop members are' provided atthe opposite end of each cylinder, comprising a member 125 threaded inthe end of the cylinder and provided with a stop block 126 on the innerend thereof, and a lock nut 127, whereby after adjustment of the screwby the knurled knob 128, the parts may be locked in position. By thisarrangement it will be seen that a short longitudinal movement of therack bars will effect a short feed increment of the saddle and a longmovement of the rack bars will effect a longer feed increment in thesaddle.

As it is customary to have any infeeding relative to a grinding wheeltake place at the end of a cutting or grinding stroke, means have beenprovided for effecting reciprocation of the rack bars at the same timethat reversal of the table occurs. As shown in Figure 10, it will berecalled that the pressure in line 43 passes through the hydraulic motor39 and returns by line 42 to effect a feeding movement of the table inone direction, and upon reverse the pressure then flows in the line 42to the hydraulic motor and returns through line 43. From this it will beseen that lines 42 and 43 are alternately under pressure and that thechange effects reverse movement of the table. Each of these lines istherefore extended, conduit 129 forming an eX- tension of line 43, andconduit 130 forming an extension of line 42, the conduit 129 beingconnected to the port 131 formed in the right end of the rack barcylinders and the conduit 130 being connected to the port 132 formed inthe left end of the rack bar cylinders. It will be noted from Figure 10that a port 133 permanently connests together the right end of eachcylinder so that upon admission of pressure to port 131, both rack barswill be moved simultaneously to the left. Also, it will be noted thatthe port 132 is formed intermediate the left end of both cylinderswhereby pressure entering this port will simultaneously enter bothcylinders thereby shifting both rack bars simultaneously to the right.From this construction it will be seen that the shifting of the rackbars is automatically taken care of by simply reversing the direction ofmovement of the table.

The operation of the saddle feed mechanism is as follows: Uponadmittance of pressure to the port 131 both rack bars will move to theleft.

The rack bar 119 meshes directly with the trigger gear 118 therebyeffecting clockwise rotation of the gear 101. Simultaneously, the rackbar 120 will be moving toward the left effecting clockwise rotation ofthe gear 121 Which in turn Will rotate the trigger gear 118' in acounter-clockwise 'direction The pawl 106 of this gear is set oppositeto the pawl 106 so that during this counter-clockwise movement the pawlwill ratchet by the teeth of gear 118'.

Upon admission of pressure to the left end of the rack bar cylinders,the rack bar 119 will ro- 4tate the gear 118 in a counter-clockwisedirecgage ratchet teeth which will rotate the hub of the gear 103 in aclockwise direction. From this is should be seen that irrespective ofthe drection of movement of the rack bars that the final resultantmotion in the hub 103 is the same or as in the illustration given, in aclockwise direction. Thus at the end of each stroke of the table, thesaddle will be given a uni-directional feed movement to vary therelation between the tool and Work. After the tool'has been moved acrossthe work in step-by-step increments by the method just described as insurface grinding operations, the knob 111 may be rotated to change theposition of the pawls 106 and 106 which will thereby cause auni-directional feed movement in the opposite direction and make itpossible for the tool to retraverse the work in an opposite direction toeffect a finishing operation.

From the description just given it will be seen that a feed movement Wasimparted to the saddle at the end of each table stroke but if so desiredthe members 125 may be moved toward one another where they willsimultaneously abut the opposite ends of either piston therebypreventing its movement and thus reducing the amount of feed imparted tothe saddle by permitting the feeding movement to take place after eachreciprocation of the table rather than at the end of each stroke of thetable. The direction of this feeding movement may again be determined bythe position of the rotatable knob 111 which determines the setting ofthe pawls 106 and 106.

From the foregoing it should now be seen that an improved grindingmachine has been providedl which is especially suitable for surfacegrinding operations and which is provided with an improved hydraulictransmission which is practically infinitely variable between its upperand lower limits and which is provided with a cross feed mechanismwhereby large increments of feed may be quickly obtained withoutincrease in table stroke.

What is claimed is:

v 1. A grinding machine having a bed, a grinding wheel journaled on thebed, a saddle reciprocably mounted on the bed, a work support mountonthe saddle for reciprocation relative'to the grinding wheel, atransmission casing depending from the saddle, means mounted in thecasing to effect reciprocation of the Work support including a rotatablemember, an hydraulic motor for effecting rotation of said member, apump, means coupling the pump to the motor, a. prime mover mounted onthe casing for actuating said pump, a throttle valve between the pumpand motor, and manual means on the exterior wall of the casing foradjusting said valve to determine the ratevof rotation of said motor andthereby the rate of movement of the work support.

2. A grinding machine having a bed, a grinding wheel and a saddlemounted on the bed for relative adjustment with respect to each other,and a work support mounted on the saddle for reciprocating Work relativeto the grinding Wheel, a transmission casing depending from the saddlehaving a reservoir in the bottom thereof, means to effect reciprocationof the work support including a rotatable member, an hydraulic motor foreffecting rotation of said member, a prime mover, a pump actuated by theprime mover, said pump having an inlet connected to the reservoir and anoutlet, means coupling the outlet to the motor including a throttlevalve and a relief valve, means to adjust the relief valve to determinethe pressure in the system and manually operated means including a rackand pinion for adjusting said throttle valve to determine the rate ofmovement of the Work support.

3. A grinding machine having a bed, a grinding wheel journaled on thebed, a saddle reciprocably mounted on the bed for relative movement withrespect to the grinding wheel, a work support mounted on the saddle forfeeding work past the grinding wheel, a transmission housing dependingfrom the saddle having a reservoir formed in the bottom thereof, meansto effect reciprocation of the work support including a rotatablemember, an hydraulic motor for effecting rotation of said member, aprime mover, a pump actuated by the prime mover, said pump having aninlet through which fluid is drawn from the reservoir and delivered tothe motor, means coupling the pump to the motor including a reliefvalve, a throttle valve and a reverse valve in the order recited, meansto adjust the relief valve to determine the pressure in the system, amanual control on the front wall of the casing for adjusting thethrottle to determine the rate of movement of the work support, areverse control lever mounted on the top of the saddle adjacent the endof the table for shifting said reverse valve either manually orautomatically.

f1. A machine tool having a bed, a grinding wheel journaled on the bed,a saddle mounted on the bed for adjustment relative to the wheel, a Worksupport reciprocably mounted on the saddle, a shaft journaled in thesaddle, means coupling one end of the shaftto the table, a driven gearrotatably mounted on the shaft and a. transmission housing dependingfrom the saddle having a self-contained hydraulically actuatedtransmission mounted therein, said transmission terminating in a drivinggear adapted to mesh with the driven gear upon assembly of the housingto the saddle to thereby couple the transmission to the table foractuation thereby.

5. A machine tool having a bed, a grinding wheel journaled thereon, asaddle adjustably mounted on the bed for movement relative to thegrinding wheel, means to effect said saddle adjustment, a tablereciprocably mounted on the saddle, a transmission housing dependingfrom the saddle having a reservoir -in the bottom thereof, anhydraulically actuated transmission in the housing including' a pump, aprime move!` for actuating said pump, an hydraulic motor driven by thepump, means coupling the motor to the table for actuation thereby, aremovable plug in the saddle for filling said reservoir, a gauge glassmounted in the front wall of said housing for determining the amount ofoil in the reservoir and a drain plug in the bottom of said casing forwithdrawing the oil therefrom.

6. In a machine tool having a translatable member, a power transmissionfor effecting movement of the member including an hydraulically actuatedmotor, hydraulic means for actuating said motor, including a pump, aprime mover for actuating said pump, a throttle valve coupling the pumpto the prime mover, means to shift said throttle valve to change therate of rotation of the motor including a shaft, a rack and pinionconnection between the shaft and valve plunger,

a control knob keyed to the shaft, a fixed dial associated with theknobv having rate indicating indicia thereon, a lock nut for securingthe shaft and valve in adjusted position, a mechanical transmissionextending from the hydraulic motor to the translatable member and aselector clutch for coupling the motor to said transmission foractuation at the selected rate.

7. In a machine tool having a translatable support, a power transmissionfor effecting movement of said support in various cycles including anhydraulic motor, means coupling the motorto said support, a prime mover,a pump actuated by the prime mover for supplying pressure to the motor,a reverse valve interposed between the pump and motor, said reversevalve having a neutral position and a power transmitting position oneach side thereof and selector means effective on the reverse valve toobtain a continuous reciprocating cycle of movement in the support, asingle reciprocation with a stop at the left end, a single reciprocationwith a stop at the right end, or a movement in a given direction andstop.

8. A'grinding machine having a bed, a grinding wheel journaled on thebed, a work table mounted on the bed for reciprocation relative to thewheel, power means for effecting said reciprocation including anhydraulic motor, a pump, a prime mover for effecting rotation of thepump to supply pressure to the motor, valve means interposed between thepump and motor for determining the rate and direction of movement of thework support, transmission gearing coupling the motor to the tableincluding a rotatable shaft, rack and pinion means coupling the shaft tothe table, a pair of spiral'gears one of which is mounted for freerotation on the shaft and the other secured to the motor shaft, a clutchmember fixed to the shaft and engageable with the spiral gears thereonto effect reciprocation of the table by the motor, a gear train, manualmeans for actuating said train, means to shift said clutch intooperative engagement with the train for manual reciprocation of thetable, detent means for maintaining the shaft in either powertransmitting position and additional detent means for maintaining saidclutch in a neutral position whereby the table may4 be manually shiftedby direct pressure without interference from the gear train or thehydraulic motor.

9. In a machine tool having a saddle and a translatable support mountedthereon, a power transmission for effecting movement of said support invarious cycles including an hydraulic motor, means coupling the motor tosaid support, a prime mover, a pump actuated by the prime mover forsupplying pressure to the motor, a reverse valve interposed between thepump and motor, said reverse valve having a neutral position and a powertransmitting position on each side thereof, said valve having a plungerprojecting therefrom, v a reverse lever pivotally mounted on the saddle,a cycle selector drum coupling the reverse lever to the valve plunger,said drum being rotatable toua plurality of positions to effect aplurality of different cycles of operation of the table and means toadjust the drum from a plurality of operating positions at the machine.

10. In a machine tool having a translatable support, a powertransmission for effecting movement of said support in various cyclesincluding an hydraulic motor, means coupling the motor to said support,a prime mover, a pump actuated by the prime mover for supplying pressureto the motor, a reverse valve interposed between the pump and motor,said reverse valve having a neutral position and a power transmittingposition on each side thereof, said'valve having a plunger projectingtherefrom, a reverse lever pivotally mounted adjacent the support, acycle selector drum coupling the reverse lever to the Valve plunger,said drum being rotatable to a plurality of positions to effect aplurality of different cycles of operation of the support, means toadjust the drum from either the front or rear of the machine, meansassociated with the drum to indicate the particular cycle correspondingto the position in which it is set, and detent means for maintaining thedrum in any selected position.

11. In a machine tool having a saddle and a translatable support mountedthereon, a power transmission for effecting movement of said support invarious cycles including an hydraulic motor, means coupling the motor tosaid support, a prime mover, a pump actuated by the prime mover forsupplying pressure to the motor, a reverse valve interposed between thepump and motor, said reverse valve having a neutral position and agpowertransmitting position on each side thereof, said valve having a plungerprojecting therefrom, a reverse lever pivotally mounted on the saddle, acycle selector drum coupling the reverse lever to the valve plunger,said drum being rotatable to a plurality of positions to effect aplurality of different cycles of operation of the support, means toadjust the drum from a plurality of positions at the machine, said drumbeing mounted on a rotatable shaft extending parallel with the supportand .slidably mounted on the saddle, the ends of said shaft projectingbeyond the sides of the saddle, indicator means on either end of theshaft showing the position to which the drum is set and manual means oneach end of the shaft for rotating the drum to a new position.

12. In a machine tool having a saddle and a translatable support mountedthereon, a power transmission for effecting movement of said support invarious cycles including an hydraulic motor, means coupling the motor tosaid support, a prime mover, a'pump actuated by the prime mover forsupplying pressure to the motor, a reverse valve interposed between thepump and motor, said reverse valve having a neutral position and a powertransmitting position on each side thereof, said valve having a plungerprojecting therefrom, a reverse lever pivotally mounted on Athe saddle,a cycle selector drum coupling the reverse lever to the valve plunger,said drum being rotatable to a plurality of positions to effect aplurality of different cycles of operation of the support, means toadjust the drum from a plurality of loperating stations at the machine,said drum being mounted on a rotatable shaft extending parallel with thesupport and slidably mounted on the saddle, the ends of said shaftprojecting beyond the sides of the saddle, indicator means on either endof the shaft showing the position to which the drum is set, manual meanson each end of the shaft for rotating the drum to a new position, crankmeans engaging each end of the shaft, and manual control meansoperatively connected with each of said crank means for effectingreciprocation of the shaft and thereby direct operation of the reversingvalve to control the movement of the support.

13. A transmission and control mechanism f or a machine tool having anhydraulically actuated transmission including a reverse valve having aneutral position and a power transmitting position on either sidethereof, trip mechanism for shifting said valve including a rotatabledrum, a peripheral groove in said drum, an operating pin coupled to thevalve and extending into said groove, detent means for positioning saiddrum in a plurality of positions, notches formed in the side of saidgroove to permit lost motion between the drum and the valve operatingpin, a reverse control lever operatively coupled with the drum, load andfire mechanism associated with said lever and operable when a notch insaid groove was in a position to receive said pin to fire the valve fromone power transmitting position to the other, but only operable to movethe valve to a neutral position when there were no notches in the grooveopposite the pin.

14. A machine tool having a bed, a grinding Wheel journaled on the bed,a saddle adjustably mounted on the bed for movement toward and from thegrinding wheel, a table reciprocably mounted on the saddle for movementtransversely of the grinding wheel, hydraulic means for effectingreciprocation of the table including a rotatable hydraulic motor, meansto effect transverse adjustment of the saddle including a rotatablemember, duplicate hydraulically actuated mechanisms for alternatelyeffecting rotation of said member each of said hydraulically actuatedmechanisms being coupledvin parallel relationship with said hydraulicmotor whereby upon reversal of ow to the motor, each of said mechanismswill be actuated but only one will be effective to feed the tablelaterally of the grinding wheel.

15. A machine tool having a bed, a grinding wheel journaled on the bed,a saddle adjustably mounted on the bed for movement toward and from thegrinding wheel, a table mounted on the saddle for reciprocationlaterally of the grinding wheel axis, hydraulic means for reciprocatingthe table including a rotatable hydraulic motor, a pump for supplyingpressure to the motor, parallel lines extending to the motor, means toalternately couple each line with pressure to thereby change thedirection of rotation of the motor and thereby reciprocation of *hetable, saddle feeding mechanism including a feed screw, a pair oftrigger gears, rack and pinion means for rotating said gears, said racksbeing reciprocably mounted in cylinders, means to couple one end of eachcylinder with one of said parallel lines, means to couple the other endof said cylinder with the other of said parallel lines, means couplingthe trigger gears with said lead screw whereby upon simultaneousreciprocation of said rack bars one of said trigger gears will effectrotation of the lead screw whereby the table will be moved laterally atthe end of each stroke, and means to vary the extent of movement of eachrack bar whereby the feeding movement of the saddle at one reverse-ofthe table may be varied with respect to the feeding movement at the'nately couple each line with pressure to thereby of the lead screw andupon simultaneous movement in the opposite direction the other of saidtrigger gears will eect rotation of the lead screw whereby the tablewill be moved lateraly at the end of each stroke, and means tosimultaneously change the ratchets of said trigger gears whereby eachwill effect in alternate succession a feeding movement of the saddle ina reverse direction.

1'7. In a machine tool having a tool spindle and a translatablesupportmovable transversely of the spindle, the combination of a powertransmission for moving the support in various cycles including a rotaryhydraulic motor, means coupling the motor to said support, a primemover, a pump actuated by the prime mover for supplying fluid pressureto the motor, a reverse valve interposed between the pump and motor,said reverse valve having a neutral position in which all flow to themotor is terminated, and a power transmitting position on each sidethereof for determining the direction of flow to the motor and therebythe direction of movement of the support, a trip controlled member forshifting the valve from either power transmitting position to a neutralposition, or the other power transmitting position, adjustable means forselectively connecting the valve positively to said trip controlledmember when it is desired to shift the valve to a neutral position aftermovement of the support in a given direction, or impositive- 1y connectthe valve to said member when it is desired to effect a reversal in thedirection of movement of the table after movement in a given direction.

18. In a machine tool having a bed, a rotatable tool spindle carried bythe bed, a saddle and a table reciprocably mounted on the saddle, thecombination of a power transmission for effecting movement of the tabletransversely of the spindle in various cycles including a rotatablehydraulic motor, transmission mechanism coupling the motor tothe table,a prime mover, a pump actuated by the prime mover for supplying fluidunder pressure to the motor, a reverse valve interposed between the pumpand motor said reverse valve having an axially shiftable plunger movableto a central position for terminating all ow to the motor and therebystopping the table; to a position on each side thereof for effectingrotation of the motor in opposite directions and thereby differentdirections of movement of the work support, a shifter mounted parallelto the valve for shifting the plunger thereof, a trip lever pivotallymounted on the saddle adjacent the table, a trip dog carried by thetable for automatically actuating said lever, said lever beingpositively connected to said shifter, and adjustable means forpositively connecting the shifter to said valve plunger for movementthereof to a neutral position upon dog actuation of the lever or formpositively connecting the shifter to the plunger to cause movement ofthe valve to the opposite power transmitting position to effect anautomatic reversal in the direction of movement of the table upon dogactuation of said plunger.

19. Ina machine tool having a saddle and a translatable support mountedthereon, the combination of a power transmission for effecting movementof said support in various cycles including an hydraulic motor, meanscoupling the motor to said support, a prime mover, a pump actuated bythe prime mover for delivering uid under pressure to the motor, areverse valve interposed between the pump and motor, said reverse valvehaving a neutral position and a power transmitting position on each sidethereof, a trip actuated control lever for said valve pivotally mountedon the saddle, a cycle selector drum coupling the lever to said valve,said drum being rotatable to a plurality of positions to effect aplurality of different connections with the valve including a pin andgroove connection, depressions formed in the sides of the groove forproviding lost motion between the parts, means to rotate the drum to afirst position to provide lost motionbetween one side of the pin and thegroove to effect reversal of the table after movement in one direction;to a second position to provide lost motion on the opposite side of thepin with respect to the groove to effect reversal of the table aftermovement in an opposite direction; to a third position to provide lostmotion on both sides of the pin with respect to the groove to effectreversal of the table at the end of each stroke thereof, and a fourthposition providing no lost motion between the pin and groove whereby thetable willstop at the end of each stroke thereof.

20. In a machine tool having a saddle and a translatable support mountedthereon, the combination of a power transmission for effecting movementof said support in various cycles including an hydraulic motor, meanscoupling the motor to said support, a prime mover, a pump actuated bythe prime mover for delivering fluid under pressure to the motor, areverse valve interposed between the pump and motor, said reverse valvehaving a neutral position and a power transmitting position on each sidethereof, a trip actuated control lever for said valve pivotally mountedonfthe saddle, a cycle selector drum coupling the lever to said valve,said drum being rotatable to a plurality of positions to effect aplurality of different connections with the valve including a pin andgroove connection, depressions formed in the sides of the groove forproviding lost motion between the parts, means to rotate the drum to afirst position to provide lost motion between one side of the pin andthe groove to effect reversal of the table after movement in onedirection; to a second position to provide lost motion on the oppositeside of the pin with respect to the groove to effect reversal of thetable after movement in an opposite direction; to a third position toprovide lost motion on both sides of the pin with respect to the grooveto effect reversal of the table at the end of each stroke thereof, afourth position providing no lost motion between the pin and groovewhereby the table will stop at the end of each stroke thereof, manualmeans for actuating said table, and a clutch for selectively connectingthe manual operating means or the motor to said table.

21. In a machine tool having a saddle and a translatable support mountedthereon, the combination of a power transmission for effecting movementof said support in various cycles including an hydraulic motor, meanscoupling the motor to said support, a prime mover, a pump actuated bythe prime mover for delivering uid under pressure to the motor, areverse valve interposed between the pump and motor, said reverse valvehaving a neutral position and a power transmitting position on each sidethereof, a trip actuated control lever for said valve pivotally mountedon the saddle, a cycle selector drum coupling the lever to said valve,said drum being rotatable to a plurality of positions to effect aplurality of different connections with the valve including a pin andgroove connection, depressions formed in the sides of the'groove forproviding lost motion between the parts, means to rotate the drum to arst position to provide lost motion between one side of the pin and thegroove to effect reversal of the table after movement in one direction;to a second position to provide'lost motion on the opposite side of thepin with respect to the groove to eiect reversal of the table aftermovement in an opposite direction; to a third position to provide lostmotion on both sides of the pin with respect to the groove to eiectreversal of the table at the end of each stroke thereof, a fourthposition providing no lost motion between the pin and groove whereby thetable will stop at the end of each stroke thereof, manual means foractuating said table, a clutch for selectively connecting the manualoperating means or the motor to said table, and means for locking saidlever in a fixed position during manual operation of the table wherebythe same will act as a fixed stop for limiting the movement in eitherdirection of the table.

HERMAN R. ISLER.

